US4957517A - Sound attenuating liquid-gas separator - Google Patents

Sound attenuating liquid-gas separator Download PDF

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Publication number
US4957517A
US4957517A US07/345,147 US34514789A US4957517A US 4957517 A US4957517 A US 4957517A US 34514789 A US34514789 A US 34514789A US 4957517 A US4957517 A US 4957517A
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United States
Prior art keywords
oil
shell
separator element
flow path
downstream
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US07/345,147
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English (en)
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Peter J. Linnert
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JPMorgan Chase Bank NA
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American Standard Inc
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Assigned to AMERICAN STANDARD INC., A CORP. OF DE. reassignment AMERICAN STANDARD INC., A CORP. OF DE. ASSIGNMENT OF ASSIGNORS INTEREST. Assignors: LINNERT, PETER J.
Priority to US07/345,147 priority Critical patent/US4957517A/en
Priority to CA000603655A priority patent/CA1305075C/en
Priority to DE4008882A priority patent/DE4008882A1/de
Priority to GB9008658A priority patent/GB2231818B/en
Priority to JP2106684A priority patent/JPH02301696A/ja
Priority to FR909005448A priority patent/FR2646475B1/fr
Priority to IT47901A priority patent/IT1240816B/it
Publication of US4957517A publication Critical patent/US4957517A/en
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Assigned to CHEMICAL BANK, AS COLLATERAL AGENT reassignment CHEMICAL BANK, AS COLLATERAL AGENT ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: AMERICAN STANDARD INC.
Assigned to AMERICAN STANDARD, INC. reassignment AMERICAN STANDARD, INC. RELEASE OF SECURITY INTEREST (RE-RECORD TO CORRECT DUPLICATES SUBMITTED BY CUSTOMER. THE NEW SCHEDULE CHANGES THE TOTAL NUMBER OF PROPERTY NUMBERS INVOLVED FROM 1133 TO 794. THIS RELEASE OF SECURITY INTEREST WAS PREVIOUSLY RECORDED AT REEL 8869, FRAME 0001.) Assignors: CHASE MANHATTAN BANK, THE (FORMERLY KNOWN AS CHEMICAL BANK)
Assigned to AMERICAN STANDARD, INC. reassignment AMERICAN STANDARD, INC. RELEASE OF SECURITY INTEREST Assignors: CHASE MANHATTAN BANK, THE (FORMERLY KNOWN AS CHEMICAL BANK)
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Expired - Fee Related legal-status Critical Current

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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01N—GAS-FLOW SILENCERS OR EXHAUST APPARATUS FOR MACHINES OR ENGINES IN GENERAL; GAS-FLOW SILENCERS OR EXHAUST APPARATUS FOR INTERNAL COMBUSTION ENGINES
    • F01N1/00—Silencing apparatus characterised by method of silencing
    • F01N1/02—Silencing apparatus characterised by method of silencing by using resonance
    • F01N1/023—Helmholtz resonators
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B01—PHYSICAL OR CHEMICAL PROCESSES OR APPARATUS IN GENERAL
    • B01D—SEPARATION
    • B01D19/00—Degasification of liquids
    • B01D19/0073—Degasification of liquids by a method not covered by groups B01D19/0005 - B01D19/0042
    • B01D19/0078—Degasification of liquids by a method not covered by groups B01D19/0005 - B01D19/0042 by vibration
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01N—GAS-FLOW SILENCERS OR EXHAUST APPARATUS FOR MACHINES OR ENGINES IN GENERAL; GAS-FLOW SILENCERS OR EXHAUST APPARATUS FOR INTERNAL COMBUSTION ENGINES
    • F01N1/00—Silencing apparatus characterised by method of silencing
    • F01N1/02—Silencing apparatus characterised by method of silencing by using resonance
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01N—GAS-FLOW SILENCERS OR EXHAUST APPARATUS FOR MACHINES OR ENGINES IN GENERAL; GAS-FLOW SILENCERS OR EXHAUST APPARATUS FOR INTERNAL COMBUSTION ENGINES
    • F01N1/00—Silencing apparatus characterised by method of silencing
    • F01N1/08—Silencing apparatus characterised by method of silencing by reducing exhaust energy by throttling or whirling
    • F01N1/12—Silencing apparatus characterised by method of silencing by reducing exhaust energy by throttling or whirling using spirally or helically shaped channels
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01N—GAS-FLOW SILENCERS OR EXHAUST APPARATUS FOR MACHINES OR ENGINES IN GENERAL; GAS-FLOW SILENCERS OR EXHAUST APPARATUS FOR INTERNAL COMBUSTION ENGINES
    • F01N3/00—Exhaust or silencing apparatus having means for purifying, rendering innocuous, or otherwise treating exhaust
    • F01N3/02—Exhaust or silencing apparatus having means for purifying, rendering innocuous, or otherwise treating exhaust for cooling, or for removing solid constituents of, exhaust
    • F01N3/037—Exhaust or silencing apparatus having means for purifying, rendering innocuous, or otherwise treating exhaust for cooling, or for removing solid constituents of, exhaust by means of inertial or centrifugal separators, e.g. of cyclone type, optionally combined or associated with agglomerators
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
    • F04C29/02—Lubrication; Lubricant separation
    • F04C29/026—Lubricant separation
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
    • F04C29/06—Silencing
    • F04C29/061—Silencers using overlapping frequencies, e.g. Helmholtz resonators
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01N—GAS-FLOW SILENCERS OR EXHAUST APPARATUS FOR MACHINES OR ENGINES IN GENERAL; GAS-FLOW SILENCERS OR EXHAUST APPARATUS FOR INTERNAL COMBUSTION ENGINES
    • F01N2230/00—Combination of silencers and other devices
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01N—GAS-FLOW SILENCERS OR EXHAUST APPARATUS FOR MACHINES OR ENGINES IN GENERAL; GAS-FLOW SILENCERS OR EXHAUST APPARATUS FOR INTERNAL COMBUSTION ENGINES
    • F01N2450/00—Methods or apparatus for fitting, inserting or repairing different elements
    • F01N2450/22—Methods or apparatus for fitting, inserting or repairing different elements by welding or brazing
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01N—GAS-FLOW SILENCERS OR EXHAUST APPARATUS FOR MACHINES OR ENGINES IN GENERAL; GAS-FLOW SILENCERS OR EXHAUST APPARATUS FOR INTERNAL COMBUSTION ENGINES
    • F01N2490/00—Structure, disposition or shape of gas-chambers
    • F01N2490/20—Chambers being formed inside the exhaust pipe without enlargement of the cross section of the pipe, e.g. resonance chambers
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02T—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO TRANSPORTATION
    • Y02T10/00—Road transport of goods or passengers
    • Y02T10/10—Internal combustion engine [ICE] based vehicles
    • Y02T10/12—Improving ICE efficiencies

Definitions

  • the present invention relates generally to the art of compressing a gas. More particularly, the present invention relates to the compression of a refrigerant gas into which a liquid is injected during the compression process. With still more particularity, the present invention relates to the requirement to separate entrained oil from the oil-gas mixture discharged by a compressor in a refrigeration circuit. Finally, the present invention relates to apparatus for centrifugally separating entrained oil from the mixture of compressed refrigerant gas and atomized oil discharged from a screw compressor in a refrigeration circuit as well as to integral apparatus for abating the noise associated therewith.
  • Compressors are employed in refrigeration circuits to raise the pressure of a refrigerant gas from a suction to a discharge pressure which permits the refrigerant to be used within the circuit to cool a desired medium.
  • compressors including rotary screw compressors, are commonly employed to compress the refrigerant gas in a refrigeration circuit.
  • the compressor housing has a low pressure end which includes a suction port and a high pressure end which includes a discharge port.
  • refrigerant gas at suction pressure enters the low pressure end of the compressor housing and is there enveloped in a pocket formed between the rotating complimentary screw rotors.
  • the volume of the gas pocket decreases and the pocket is circumferentially displaced as the compressor rotors continue to rotate and mesh.
  • the gas within such a pocket is compressed, and therefore heated, by virtue of the decreasing volume in which it is contained, prior to the pocket's opening to the discharge port.
  • the pocket as it continues to decrease in volume, eventually opens to the discharge port in the high pressure end of the compressor housing and the compressed gas is discharged from the compressor's is working chamber.
  • Screw compressors used in refrigeration applications will, in the large majority of instances, include an oil injection feature. Oil is injected into the working chamber of the compressor, and therefore into the refrigerant gas being compressed therein for several reasons. First, the injected oil acts to cool the refrigerant gas undergoing compression. As a result, the compressor rotors are themselves cooled allowing for tighter tolerances, in the first instance, between the rotors and between the rotors and the rotor housing which defines the working chamber.
  • oil injected into the working chamber of a screw compressor acts as a lubricant.
  • One of the two rotors in a screw compressor is normally driven by an external source, such as an electric motor, with the other rotor being driven by virtue of its meshing relationship with the externally driven rotor.
  • the injected oil transmits the drive force and prevents excessive wear between the driving and driven rotors.
  • oil injected into the working chamber of a screw compressor acts as a sealant between the meshing rotors and between the rotors and the working chamber in which they are contained in the compressor housing.
  • the oil so injected creates a barrier in the various higher to lower pressure leakage paths which exist within a screw compressor and allows for tighter initial machining tolerances and/or increased efficiency within the compressor.
  • Oil injected into the working chamber of a screw compressor is atomized and becomes entrained in the refrigerant gas undergoing compression.
  • Such oil must be removed from the oil-rich mixture discharged from the compressor in order to make the oil available for reinjection into the compressor for the purposes enumerated above. Further, removal of excess injected oil must be accomplished to insure that the performance of the refrigerant gas is not adversely affected within the refrigerant circuit.
  • Screw compressors have proven to be particularly suited for use in large capacity refrigeration systems with application in 40 to 400-ton systems being common.
  • the size of such compressors and the amount of oil injected thereinto is significant. Injection of one part oil for every five parts of circulated refrigerant by weight coupled with a requirement to remove 90% or more or the injected oil immediately upon discharge of the mixture from the compressor working chamber is typical.
  • the refrigeration equipment including the liquid-separation apparatus, is preferably hermetically or semi-hermetically sealed.
  • Liquid-gas separators have historically comprised large separator receiver combinations which have included, in many instances, baffle schemes to facilitate liquid-gas separation. Such schemes are, as indicated in U.S. Pat. No. 3,917,474 to Heckenkamp et al., neither simple nor inexpensive to fabricate. Further, many such units call for the separator element to be removable in order to allow for its cleaning or replacement.
  • Exemplary of a second liquid-gas separator for screw compressor applications is that found in U.S. Pat. No. 4,622,048, assigned to the assignee of the present invention and which is incorporated herein by reference. That patent, together with U.S. Pat. Nos. 4,662,190 and 4,762,469 which are likewise assigned to the assignee of the present invention and which are likewise incorporated herein by reference, disclose oil separator portions in a screw compressor assembly having a centrifugal oil separator element which is permeable along its entire length.
  • centrifugal oil separators of the immediately aforementioned patents have proven to be extremely efficient, those designs do not specifically include nor contemplate integral noise attenuation and abatement in general or with respect to certain frequencies in particular.
  • Such noise is characteristic of compressors in general and of screw compressors in particular.
  • Factors in the production of compressor noise including the frequency of the power used to energize the motor (50 cycle versus 60 cycle), the capacity of the compressor, and, in screw compressors, the number of lobes on the male screw rotor which is typically the driven rotor.
  • the combined oil separator and noise attenuation apparatus of the present invention includes a hermetically sealed sump housing in which a separator element including nested muffler elements are disposed.
  • the separator element includes an outer cylindrical shell and defines an inlet and an outlet disposed generally on opposite ends of the shell.
  • the inlet of the separator element is in flow communication with the discharge port of the compressor and the separator element therefore receives the oil-gas mixture discharged from the compressors working chamber directly.
  • the outlet of the separator element is in flow communication with but is physically separated from a discharge conduit which directs relatively dry refrigerant gas, from which oil has been separated, out of the oil separator portion of the compressor assembly.
  • the separator element includes an inner generally cylindrical column having an open-ended extension in which the discharge conduit is concentrically nested.
  • the nesting of the cylindrical extension and discharge conduit internal of the separator element together with their physical separation reduces the amount of noise produced in and transmitted from the oil separator portion.
  • the nested components of the separator are dimensioned and spaced apart so as to be “tuned”, in accordance with the characteristics of the size/capacity of the compressor with which they are used, to reduce and/or eliminate noise at certain predetermined frequencies which are characteristic of that size/capacity compressor.
  • the outer shell of the separator element defines a plurality of apertures of a predetermined size and shape located at the downstream end of the separator shell and through which oil separated from refrigerant gas passes to an oil sump.
  • the separator element includes, in addition to the shell, a helical ramp disposed around the inner column both of which are mounted generally co-axially within the solid portion of the separator shell.
  • a helical passage is therefore formed within the solid walled portion of the separator shell through which a received oil-refrigerant mixture is constrained to pass between the separator element inlet and outlet.
  • This passage is defined by the solid interior wall portion of the separator shell, the helical ramp and the central column about which the helical ramp winds within the oil separator element.
  • the aforementioned open-ended cylindrical extension extends downstream from the inner column about which the helical ramp winds.
  • Liquid separated as a result of the swirling motion imparted to the mixture is carried along the solid inner wall of the shell to the downstream end of the shell where it passes through the shell holes defined therein and drains into the sump.
  • the refrigerant gas undergoes a first generally 180° turn within the separator element around the open downstream end of the cylindrical extension and then a second generally 180° turn within the separator element around the open upstream end of the discharge conduit in order to pass out of the oil separator portion of the compressor assembly through the discharge conduit.
  • the directional changes in the refrigerant flow path cause the further disentrainment of oil which remains in the gas with the result that the refrigerant gas passing out of the discharge conduit is relatively free of entrained oil.
  • the discharge conduit is physically separated from the oil separator element and is itself concentrically housed by the cylindrical extension of the central column of the oil separator element and because the cylindrical extension of the inner column and the discharge conduit are nested and are specifically dimensioned or tuned to eliminate or abate the production of noise in general and at predetermined frequencies in particular, a muffling effect is achieved within the oil separator portion of the compressor assembly which significantly diminishes the noise produced within and transmitted from the compressor assembly.
  • FIG. 1 is a cross sectional view of the screw compressor assembly of the present invention.
  • FIG. 2 is a partial cross sectional view of the oil separator portion of the assembly of FIG. 1 illustrating the flow path of refrigerant gas and oil therethrough.
  • FIG. 3 is a sectional view taken along line 3--3 of FIG. 1.
  • FIG. 4 illustrates an alternative embodiment of the helical ramp portion of the oil separator of the present invention.
  • FIG. 5 is a view taken along line 5--5 of FIG. 2.
  • a refrigeration system 10 includes a screw compressor assembly 12 which is comprised of a compressor section 14 and an oil separator section 16. Refrigeration system 10 further includes, typically, a condenser 18, an expansion device 20 and an evaporator 22. Compressed refrigerant gas, from which oil has been separated, is directed from oil separator section 16 of compressor assembly 12 to condenser 18 where it is condensed and becomes a low temperature, high pressure liquid.
  • the refrigerant is directed to expansion device 20 where it becomes a low temperature, low pressure liquid by the process of expansion.
  • the low pressure, low temperature liquid refrigerant next enters evaporator 22 where it is vaporized and becomes a low pressure, low temperature gas prior to being returned to compressor section 14.
  • Compressor section 14 includes a rotor housing 24 which defines a suction area 26 into which vaporized low pressure refrigerant gas is communicated from evaporator 22.
  • Rotor housing 24 also defines a suction port 28 through which such gas is admitted to compressor working chamber 30 in which screw rotors 32 and 34 are housed.
  • Suction area 26 Attached to the driven one of rotors 32 and 34 is motor 36 which drives shaft 38 on which the driven rotor is mounted.
  • Suction area 26 in the preferred embodiment, includes suction subareas 40 and 42 all of which are in flow communication with rotor housing 24.
  • Rotor housing 24 also defines an opening 44 into suction subarea 42, the purpose of which will later be described.
  • Rotor housing 24 further includes a discharge port 46 through which compressed refrigerant gas is discharged from working chamber 30.
  • a slide valve 48 Disposed within rotor housing 24 and cooperating therewith to define working chamber 30 is a slide valve 48.
  • Slide valve 48 is axially moveable with respect to rotors 32 and 34 within rotor housing 24. In the position illustrated in FIG. 1, working chamber 30 is in flow communication with suction subarea 40 of suction area 26 as well as with main suction area 26 through suction port 28.
  • Slide valve 48 is positionable between a first position in which low pressure end face 50 of the slide valve abuts stop 52 of rotor housing 24 and a second position in which the degree to which rotors 32 and 34 are exposed to suction subarea 40 is at a maximum.
  • Oil separator section 16 includes a centrifugal oil separator element 54 disposed within sealed oil sump housing 56.
  • a bearing housing 58 defining a discharge passage 60 is disposed between the discharge port 46 of rotor housing 24 and separator element 54.
  • Separator element 54 defines an inlet 62 in flow communication with passage 60 of bearing housing 58 and includes an outer cylindrical shell 64 which cooperates with inner cylindrical column 66 and ramp 68 to define a helical passage between inlet 62 and outlet 70 of sump housing 56.
  • Inner cylindrical column 66 in the preferred embodiment, accommodates a pressure housing 72 in which piston 74 and spring 76 are disposed. Piston 74 and pressure housing 72 cooperate to define a pressure chamber 78 which is capable of selective flow communication with opening 44 in rotor housing 24 or with sump area 80 of oil separator 16 through opening 82 in sealed sump housing 56.
  • Pressure chamber 78 is put into flow communication with opening 44 and suction subarea 42 by the opening of solenoid valve 84 or with sump area 80 by the opening of solenoid valve 86.
  • Housing 66 has an end cap 88 which defines an opening 90 through which the face of piston 74 opposite the face which cooperates to define chamber 78 is constantly maintained in flow communication with the remainder of the interior of oil separator element 54.
  • Body 94 is slideably mounted on the rod which connects piston 74 with an oil separator section 16 and slide valve 48 within rotor housing 24. It will be appreciated that when piston 74 moves within pressure housing 72, slide valve 48 is correspondingly moved within rotor housing 24 and further, that the movement the rod connecting the piston and slide valve does not of itself effect the movement of body 94.
  • outer shell 64 of separator element 54 defines a plurality of openings or perforations 96 in the lower portion of its downstream end. These openings cooperate to form a drain field through which oil exits separator element 54 and passes to sump 80.
  • Shell 64 and, therefore, separator element 54 are closed at their downstream ends by end plate 98 which defines an aperture into which and through generally tubular discharge conduit 100 extends.
  • the aperture defined by end plate 98 is slightly larger than the outside diameter of discharge conduit 100 so that a gap 102 is created between the edge of the aperture in end plate 98 and the exterior surface of discharge conduit 100.
  • Oil separator element 54 is therefore physically separated from discharge conduit 100 with gap 102 functioning as a barrier to the development of resonant frequencies and to the conductive transmission of sound from oil separator element 54 to or into discharge conduit 100 and sump housing 56.
  • Discharge conduit 100 is disposed, at its downstream end within outlet 70 of sump housing 56 and is fixedly connected to the sump housing as by welding or brazing.
  • sump housing 56 is attached to rotor housing 24 as by being bolted thereto and it will be appreciated that, if necessary, sump housing 56 can be unbolted from the rotor housing and removed therefrom. Upon removal of the sump housing, discharge conduit 100 is withdrawn through the aperture defined by end plate 98 of separator element 54 and the entire separator element and bearing housing is made accessible.
  • Discharge conduit 100 extends through the aperture defined by end plate 98 and a predetermined distance into the interior of separator element 54.
  • ramp 68 is disposed only in the upstream portion of separator element 54 and that inner cylindrical column 66 of separator element 54 includes a generally tubular extension 104 which extends downstream of the location at which ramp 68 ends.
  • Downstream extension 104 of inner cylindrical column 66 extends a predetermined distance toward end plate 98 of the separator element although its downstream end is physically spaced apart from the end plate.
  • Extension 104 can be an integral physical extension of column 66 or, if preferred, may be a physically separate piece attached to the downstream end of column 66.
  • Discharge conduit 100 extends concentrically into the open end of extension 104 of inner cylindrical column 66, so as to be nested therein, with upstream end 106 of discharge conduit 100 being spaced apart, at a predetermined distance, from partition 108 which partitions the interior of cylindrical column 66.
  • partition 108 is the upstream end face of pressure housing 72.
  • the oil separation apparatus of the present invention has application in screw compressor assemblies of the type illustrated in FIG. 1 wherein pressure housing 72 houses the piston actuator 74 of the slide valve assembly as well as in screw compressor assemblies in which no slide valve compressor modulation apparatus is employed in conjunction with the oil separation apparatus.
  • Partition 108 is a wall which operates as a barrier to the flow of gas in the direction it is travelling subsequent to making a first 180° turn around the open end of extension 104. That it is the downstream face of a pressure housing or simply a relatively thin-walled solid partition is immaterial with respect to the implementation of the present invention.
  • the upstream end 106 of discharge conduit 100 is nested within the downstream extension 104 of cylindrical column 66.
  • This nesting forces refrigerant gas to undergo a first 180° change in direction so as to enter the downstream open end of extension 104 and a second 180° turn so as to enter discharge conduit 100 prior to exiting the oil separator portion 16.
  • This nesting also achieves a muffling affect within the oil separator portion so that extension 104 and discharge conduit 100 can be characterized as generally tubular nested muffling means for the abatement and reduction of compressor assembly noise.
  • the muffling means are dimensioned or "tuned” to eliminate or reduce noise at particular frequencies that are characteristic of different compressor sizes and capacities. Factors which contribute to the development of noise at particular frequencies include compressor size and capacity, the frequency of the power supply driving the compressor motor and the number of lobes on the male screw rotor which is typically the rotor driven by the motor. Those frequencies and the "tuning" of the muffler means, once again, depend primarily on the specific design of a given compressor assembly as well as the characteristic frequency of the noise generated thereby and will be determined without undue difficulty, by those skilled in the art, for the particular compressor with which they are working.
  • refrigerant gas is sucked into working chamber 30 through suction port 28 by the rotation and meshing of rotors 32 and 34, one of which is driven in a predetermined direction by motor 36.
  • motor 36 When motor 36 is in operation, at least a portion of the refrigerant gas sucked in through suction port 28 into working chamber 30 is compressed and discharged through discharge port 46 no matter what the position of slide valve 48. Compressed refrigerant gas is discharged from the working chamber through discharge port 46 and into discharge passage 60 of bearing housing 58.
  • Oil stored in sump 80 is essentially at discharge pressure when the compressor assembly is in operation due to the selective permeability of wall 64 of separator element 54 at the location of the oil drain field at its downstream end.
  • the oil from sump 80 is further employed to lubricate the bearings and the bearing areas in which the ends of the shafts of rotors 32 and 34 are mounted in the compressor assembly.
  • Such lubricating oil is vented into the working chamber of the compressor after it passes through the bearings and bearing areas. Additionally, sump oil is selectively directed out of sump 80 through solenoid valve 86, when valve 86 is opened, and into pressure chamber 78 to cause the movement of piston 74 and the corresponding movement of slide valve 48 in rotor housing 24 in the embodiment of FIG. 1.
  • pressure chamber 78 is vented through solenoid valve 84 into suction subarea 42 of rotor housing 24.
  • certain screw compressor assembly embodiments include an oil injection feature, as is illustrated in U.S. Pat. No. 4,780,061, which is assigned to the assignee of the present invention and which is incorporated herein by reference, by which oil is injected directly into working chamber 30 of rotor housing 24 from sump 80.
  • the mixture of oil and refrigerant gas discharged from compressor section 14 enters oil separator portion 16 through inlet 62 and impinges on body 94
  • the mixture of refrigerant gas and oil is forced by its interaction with body 94 to undergo a smooth transition from essentially axial flow to a combination of axial and radial flow within separator element 54.
  • the mixture is next fed into swirl vanes 92 which are best illustrated in FIG. 3.
  • the vanes 92 impart an initial rotational or swirling motion to the mixture which is in a predetermined direction and which is cooperative with the orientation of the helical passage defined within separator element 54 by ramp 68, shell 64 and inner cylindrical column 66.
  • the gas, from which a majority of the oil has now been separated, is next forced to make a 180° turn around the downstream end of extension 104 of cylindrical column 66.
  • This forced directional change in combination with the impingement of the gas on end plate 98 causes the further disentrainment of any oil which remains entrained in the gas.
  • the gas is next caused to make a second 180° directional change so as to enter discharge conduit 100 and to exit the oil separator portion 16.
  • ramp 68 which is illustrated in FIGS. 1 and 2 as a unitary ramp winding through in excess of 360°, can be replaced by two or more helical members 118 and 120. These members, which wind through 360° or less, may be preferable to the use of a unitary ramp from the standpoint of cost and ease of separator element fabrication. Members 118 and 120 will typically overlap or will, to some extent, be nested within one another as is illustrated in FIG. 4.
  • FIG. 5 illustrates directing baffles 122, 124 and 126 which generally shield the drain field on the exterior of separator element 54. These baffles direct separated oil downward into sump 80 and break up the continued swirl of the oil, in the direction indicated in FIG. 5, as it exits the drain field perforations 96. Finally it should be noted that additional tuning of the oil separator element to eliminate noise at predetermined frequencies can be accomplished by adding weights, not shown, at the generally downstream end of the separator element.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Chemical Kinetics & Catalysis (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)
  • Sampling And Sample Adjustment (AREA)
US07/345,147 1989-04-28 1989-04-28 Sound attenuating liquid-gas separator Expired - Fee Related US4957517A (en)

Priority Applications (7)

Application Number Priority Date Filing Date Title
US07/345,147 US4957517A (en) 1989-04-28 1989-04-28 Sound attenuating liquid-gas separator
CA000603655A CA1305075C (en) 1989-04-28 1989-06-22 Sound attenuating liquid-gas separator
DE4008882A DE4008882A1 (de) 1989-04-28 1990-03-20 Schraubenverdichter
GB9008658A GB2231818B (en) 1989-04-28 1990-04-18 Noise abating liquid-gas separator
JP2106684A JPH02301696A (ja) 1989-04-28 1990-04-24 音減衰型液体とガスの分離装置
IT47901A IT1240816B (it) 1989-04-28 1990-04-27 Apparecchio a rumorosita' attenuata per la separazione di liquido da gas
FR909005448A FR2646475B1 (fr) 1989-04-28 1990-04-27 Appareil de separation d'huile pour compresseur a vis a attenuation de bruit

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US07/345,147 US4957517A (en) 1989-04-28 1989-04-28 Sound attenuating liquid-gas separator

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US4957517A true US4957517A (en) 1990-09-18

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US (1) US4957517A (ru)
JP (1) JPH02301696A (ru)
CA (1) CA1305075C (ru)
DE (1) DE4008882A1 (ru)
FR (1) FR2646475B1 (ru)
GB (1) GB2231818B (ru)
IT (1) IT1240816B (ru)

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US5149346A (en) * 1991-06-17 1992-09-22 The United States Of America As Represented By The Secretary Of The Navy Apparatus for reduction of vibration in liquid-injected gas compressor system
EP0540459A1 (en) * 1991-10-28 1993-05-05 Carrier Corporation Integral oil separator and muffler
US5224648A (en) * 1992-03-27 1993-07-06 American Standard Inc. Two-way wireless HVAC system and thermostat
US5479907A (en) * 1994-07-12 1996-01-02 Walker, Jr.; Robert A. Combination in-line air-filter/air-oil separator/air-silencer with preseparator
FR2816995A1 (fr) * 2000-11-23 2002-05-24 Luk Fahrzeug Hydraulik Installation de climatisation avec dispositif pour le depot du lubrifiant et compresseur
EP1344559A1 (en) * 2002-03-16 2003-09-17 Rolls-Royce Plc An air/oil separator
WO2005057014A1 (de) * 2003-12-15 2005-06-23 Bitzer Kühlmaschinenbau Gmbh Schraubenverdichter mit einem schalldämpfer
US20060124099A1 (en) * 2004-12-15 2006-06-15 Matthew Richards Oil tank for dry sump engines
EP1799973A2 (en) * 2004-09-30 2007-06-27 Carrier Corporation Compressor sound suppression
US20070234691A1 (en) * 2006-04-10 2007-10-11 Samsung Electronics Co., Ltd. Cyclone and cyclone air purifier and method of air purification thereof
US20070272176A1 (en) * 2004-03-08 2007-11-29 Reinz-Dichtungs-Gmbh Cylinder Head Cover With Oil Separator
EP1875049A1 (en) * 2005-04-11 2008-01-09 Carrier Corporation Compressor muffler
US20080078618A1 (en) * 2006-09-29 2008-04-03 Aspen Compressor, Llc Orientation and gravity insensitive in-casing oil management system for fluid displacement devices, and methods related thereto
US20080250812A1 (en) * 2005-11-30 2008-10-16 Alexander Lifson Multi-Circuit Refrigerant System Utilizing Pulse Width Modulation Techniques
US20080314063A1 (en) * 2005-12-14 2008-12-25 Alexander Lifson Combined Muffler and Oil Separator for Refrigerant System
CN102112746A (zh) * 2008-07-29 2011-06-29 比泽尔制冷设备有限公司 用于螺杆式压缩机的油分离器和消声器
ITVI20120227A1 (it) * 2012-09-11 2012-12-11 Virgilio Mietto Dispositivo di disoleazione per un compressore volumetrico e compressore volumetrico.
CN105275805A (zh) * 2014-06-27 2016-01-27 江南大学 一种喷油式双螺杆压缩机
CN105899809A (zh) * 2013-12-12 2016-08-24 Gea制冷德国公司 压缩机
CN107237664A (zh) * 2017-08-09 2017-10-10 宿州冬宇环保科技有限公司 一种公交车尾气消音净化装置
CN109952477A (zh) * 2016-11-15 2019-06-28 开利公司 具有消声器的润滑剂分离器
US10682588B2 (en) 2017-10-18 2020-06-16 Ingersoll-Rand Industrial U.S., Inc. Modular heat exchanger, moisture separator and pulsation dampener for a multi-stage fluid compressor
WO2020168876A1 (zh) * 2019-02-20 2020-08-27 安徽美芝制冷设备有限公司 消音装置和压缩机
US11994129B2 (en) * 2016-09-21 2024-05-28 Knorr-Bremse Systeme Fuer Nutzfahrzeuge Gmbh Screw compressor for a utility vehicle
US12000329B2 (en) 2018-12-17 2024-06-04 Aston Martin Lagonda Limited Assemblies for engines

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GB2277470B (en) * 1993-04-29 1997-11-05 Nash Engineering Co A separator for separating gas from a liquid
GB2344856B (en) * 1998-12-18 2002-12-18 Ingersoll Rand Company Ltd Method of operating compressor
GB2353236A (en) 1999-08-17 2001-02-21 Baker Hughes Ltd Cyclone separator with multiple baffles of distinct pitch
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Cited By (57)

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US5149346A (en) * 1991-06-17 1992-09-22 The United States Of America As Represented By The Secretary Of The Navy Apparatus for reduction of vibration in liquid-injected gas compressor system
EP0540459A1 (en) * 1991-10-28 1993-05-05 Carrier Corporation Integral oil separator and muffler
US5214937A (en) * 1991-10-28 1993-06-01 Carrier Corporation Integral oil separator and muffler
AU651013B2 (en) * 1991-10-28 1994-07-07 Carrier Corporation Integral oil separator and muffler
US5224648A (en) * 1992-03-27 1993-07-06 American Standard Inc. Two-way wireless HVAC system and thermostat
US5479907A (en) * 1994-07-12 1996-01-02 Walker, Jr.; Robert A. Combination in-line air-filter/air-oil separator/air-silencer with preseparator
WO1996001941A1 (en) * 1994-07-12 1996-01-25 Walker Robert A Jr Combination in-line air-filter/air-oil separator/air-silencer with preseparator
WO2002042645A1 (de) * 2000-11-23 2002-05-30 Luk Fahrzeug-Hydraulik Gmbh & Co. Kg Klimaanlage mit schmiermittelabscheider und verdichter
FR2816995A1 (fr) * 2000-11-23 2002-05-24 Luk Fahrzeug Hydraulik Installation de climatisation avec dispositif pour le depot du lubrifiant et compresseur
EP1344559A1 (en) * 2002-03-16 2003-09-17 Rolls-Royce Plc An air/oil separator
US20040098956A1 (en) * 2002-03-16 2004-05-27 Care Ian C. Air/oil separator
US6893478B2 (en) 2002-03-16 2005-05-17 Rolls-Royce Plc Air/oil separator
CN100526649C (zh) * 2003-12-15 2009-08-12 比泽尔制冷设备有限公司 带有消声器的螺杆压缩机
WO2005057014A1 (de) * 2003-12-15 2005-06-23 Bitzer Kühlmaschinenbau Gmbh Schraubenverdichter mit einem schalldämpfer
DE10359032A1 (de) * 2003-12-15 2005-07-14 Bitzer Kühlmaschinenbau Gmbh Schraubenverdichter
US20060243520A1 (en) * 2003-12-15 2006-11-02 Bitzer Kuehlmaschinenbau Gmbh Screw compressor with an acoustic wave damping device
US7743742B2 (en) * 2004-03-08 2010-06-29 Reinz-Dichtungs Gmbh Cylinder head cover with oil separator
US20070272176A1 (en) * 2004-03-08 2007-11-29 Reinz-Dichtungs-Gmbh Cylinder Head Cover With Oil Separator
US7993112B2 (en) 2004-09-30 2011-08-09 Carrier Corporation Compressor sound suppression
US20080260547A1 (en) * 2004-09-30 2008-10-23 Carrier Corporation Compressor sound suppression
EP1799973A4 (en) * 2004-09-30 2010-10-06 Carrier Corp REMOVING THE NOISE OF A COMPRESSOR
EP1799973A2 (en) * 2004-09-30 2007-06-27 Carrier Corporation Compressor sound suppression
US20060124099A1 (en) * 2004-12-15 2006-06-15 Matthew Richards Oil tank for dry sump engines
US7618482B2 (en) * 2004-12-15 2009-11-17 Aston Martin Lagonda Limited Oil tank for dry sump engines
EP1875049A1 (en) * 2005-04-11 2008-01-09 Carrier Corporation Compressor muffler
EP1875049A4 (en) * 2005-04-11 2011-07-06 Carrier Corp MUFFLER FOR COMPRESSORS
US7988427B2 (en) 2005-04-11 2011-08-02 Carrier Corporation Compressor muffler
US20080257640A1 (en) * 2005-04-11 2008-10-23 Carrier Corporation Compressor Muffler
US20080250812A1 (en) * 2005-11-30 2008-10-16 Alexander Lifson Multi-Circuit Refrigerant System Utilizing Pulse Width Modulation Techniques
US20080314063A1 (en) * 2005-12-14 2008-12-25 Alexander Lifson Combined Muffler and Oil Separator for Refrigerant System
US20070234691A1 (en) * 2006-04-10 2007-10-11 Samsung Electronics Co., Ltd. Cyclone and cyclone air purifier and method of air purification thereof
WO2008042667A3 (en) * 2006-09-29 2008-07-31 Aspen Compressor Llc Orientation and gravity insensitive in-casing oil management system
US7789202B2 (en) 2006-09-29 2010-09-07 Aspen Compressor, Llc. Orientation and gravity insensitive in-casing oil management system for fluid displacement devices, and methods related thereto
WO2008042667A2 (en) * 2006-09-29 2008-04-10 Aspen Compressor, Llc Orientation and gravity insensitive in-casing oil management system
US20080078618A1 (en) * 2006-09-29 2008-04-03 Aspen Compressor, Llc Orientation and gravity insensitive in-casing oil management system for fluid displacement devices, and methods related thereto
CN102112746A (zh) * 2008-07-29 2011-06-29 比泽尔制冷设备有限公司 用于螺杆式压缩机的油分离器和消声器
US20110182762A1 (en) * 2008-07-29 2011-07-28 Bitzer Kuehlmaschinenbau Gmbh Screw-Type Compressor
CN102112746B (zh) * 2008-07-29 2014-10-22 比泽尔制冷设备有限公司 用于螺杆式压缩机的油分离器和消声器
US8500424B2 (en) 2008-07-29 2013-08-06 Bitzer Kuehlmaschinenbau Screw compressor with a sound dampening device that separates lubricant
ITVI20120227A1 (it) * 2012-09-11 2012-12-11 Virgilio Mietto Dispositivo di disoleazione per un compressore volumetrico e compressore volumetrico.
RU2610974C2 (ru) * 2012-09-11 2017-02-17 Виргилио МИЕТТО Устройство отделения смазывающей жидкости, устройство для сжатия газа, содержащее это устройство отделения, и резервуар отделения для устройства сжатия
CN104736850A (zh) * 2012-09-11 2015-06-24 维尔吉利奥·米耶托 用于容积式压缩机的油分离器装置以及容积式压缩机
WO2014041407A3 (en) * 2012-09-11 2014-05-08 Virgilio Mietto Oil separator device for a volumetric compressor and volumetric compressor
CN104736850B (zh) * 2012-09-11 2017-05-10 维尔吉利奥·米耶托 分离器装置、包括分离器装置的压缩装置以及分离储罐
US9534600B2 (en) 2012-09-11 2017-01-03 Virgilio Mietto Oil separator device for a volumetric compressor and volumetric compressor
CN105899809B (zh) * 2013-12-12 2018-04-17 Gea制冷德国公司 压缩机
CN105899809A (zh) * 2013-12-12 2016-08-24 Gea制冷德国公司 压缩机
CN105275805A (zh) * 2014-06-27 2016-01-27 江南大学 一种喷油式双螺杆压缩机
CN105275805B (zh) * 2014-06-27 2018-08-07 江南大学 一种喷油式双螺杆压缩机
US11994129B2 (en) * 2016-09-21 2024-05-28 Knorr-Bremse Systeme Fuer Nutzfahrzeuge Gmbh Screw compressor for a utility vehicle
CN109952477A (zh) * 2016-11-15 2019-06-28 开利公司 具有消声器的润滑剂分离器
CN109952477B (zh) * 2016-11-15 2021-05-25 开利公司 具有消声器的润滑剂分离器
CN107237664A (zh) * 2017-08-09 2017-10-10 宿州冬宇环保科技有限公司 一种公交车尾气消音净化装置
US10682588B2 (en) 2017-10-18 2020-06-16 Ingersoll-Rand Industrial U.S., Inc. Modular heat exchanger, moisture separator and pulsation dampener for a multi-stage fluid compressor
US12000329B2 (en) 2018-12-17 2024-06-04 Aston Martin Lagonda Limited Assemblies for engines
WO2020168876A1 (zh) * 2019-02-20 2020-08-27 安徽美芝制冷设备有限公司 消音装置和压缩机
US11692562B2 (en) 2019-02-20 2023-07-04 Anhui Meizhi Compressor Co., Ltd. Silencing device and compressor

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Publication number Publication date
FR2646475B1 (fr) 1992-07-03
GB9008658D0 (en) 1990-06-13
GB2231818B (en) 1993-02-10
IT9047901A1 (it) 1991-10-27
FR2646475A1 (fr) 1990-11-02
CA1305075C (en) 1992-07-14
IT1240816B (it) 1993-12-17
JPH02301696A (ja) 1990-12-13
IT9047901A0 (it) 1990-04-27
GB2231818A (en) 1990-11-28
DE4008882A1 (de) 1990-10-31
DE4008882C2 (ru) 1992-09-24

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